Means for balancing crushers.



0. P. HOOD.

MEANS FOR BALANCING onusnms.

APPLICATION FILED FEB. 9,1908. 91 9 ,582, Patented Apr. 27, 1909.

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0. P. HOOD.

MEANS FOR BALANCING GBUSHEBS.

APPLIOATION FILED NIB. 9, 1908.

Patented Apr. 27, 1909.

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. APPLIOATIDH FILED FEB. 9, 1906. 91 9,582. Patented Apr. 27, 1909.

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O. P. HOOD.

MEANS FOR BALANCING 'GRUSHERS.

APPLICATION FILED r123. 9.190s.

Patented Apr. 27, 1909.

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invention.

UNITED stares Parana? FFIQE.

OZNI P. HOOD, OF HO UGHTON, MICHIGAN.

MEANS FOR BALANCING CRUSHERS.

Application filed February 9 To all whom it may concern.-

Be it known that I, OZNI P. 1100]), a citizen oi' the United States,residing at Houghton, in the county oi IIoughton and State of Michigan,have invented certain new and useful Improvements in Means for BalancingCrushers, of which the following is a specification.

In the operation of that type of crushers having a swinging jawoscillated by a toggle there is a horizontal vibration which is not esecially objectionable where a firm and solid foundation can be had, butwhen the crusher is arranged in the top of a rock-house, as is customaryin copper mining, the horizontal vibration becomes exceedingly ob- Theobject of my invention is to )rovide means for eliminating thishorizontal vibration.

The accompanying drawings illustrate my Figure 1 is a plan of anordinary Blake crusher equipped with an embodiment of my invention; Fig.2 is a section on line 2 2 of Fig. 1; Fig. 3 a diagram of theconstruction shown in Figs. 1 and 2; Fig. i a similar diagram of acrusher in which the oscillating jaw is given two complete oscillationsfor each rotation of the drive-shalt, and Fig. 5 force curves.

In the drawings, 10 indicates the oscillating jaw, pivoted at TV in themain frame 12. The aw 10 is oscillated by means of a toggle AB, BC whichis pivoted at C to the jaw 10 and at A on the main frame 12. Pivotcd tothe knuckle B of the toggle is one end of a pitman 15 which is connectedat the other end to the eccentric, or crank 1', which is carried by themain driveshai't 17 ournaled in the main frame parallel with the axis ofoscillation oi the crush r j aw.

The horizontal forces which require bal ancing will depend upon thevelocity of oscillation of the crusher jaw (for instance the velocity atthe point C) the mass of the oscillating carts, and their acceleration.This device 'alances the horizontal components of those forces generatedwithin the machine by inertia of the parts having variable horizontalvelocities. Thus the oscillating crusher j aw, having a variable angularvelocity about the pivot TV, will resist any change in velocity with aforce dependin upon the velocity of rotation of driving s aft 17, uponthe mass of the oscillating parts, and their Specification of LettersPatent.

Patented April 27, 1909.

Serial No. 300,225.

acceleration at any instant. The character of the motion imparted to theoscillating jaw 10 is such that the rate of change oi'movement of apoint on'the jaw, as 0, increases while shaft 17 is revolving throughonethird 01' its rotation and the rate of change decreases during theremaining two-thirds of the revolution. The resisting forces of in ertiadepend upon the acceleration or the rate of increase or decrease ofvelocity of the mass moved. While the mass oi the jaw 10 actually movesabout as a center, its ac tual movement is so small that the path of anypoint may be considered a straight line and the acceleration asstraight-line acceleration.

Curve F, Fig. 5, re resents the character ol' the acceleration of tiejaw in a machine of the type shown in Figs. 1, 2 and 3. Curve F isplotted on a hold where horizontal distances represent time and forconvenience in comparing with other curves to be drawn, this time ismeasured by the uniform angular movement 0 of the eccentric impartingmotion to the device. \Vith the eccentric at the lower dead center as astarting point and calling this 0 degrees, at this time the rate ofchange of the velocity of the jaw is greatest and is represented by thatpoint on the curve F vertically above the 0 ol' the horizontal scale.For each new angular )osition oi the eccentric there is a new rate 01change of the velocity of the jaw and this being continuously plotted,generates curve F. Since the resisting force of inertia is proportionalto this acceleration, curve F can also represent, to some suitable scaleof pounds, the horizontal shaking force which is to be balanced.

A partial balance may be obtained by introducing an unbalanced revolvingweight Q which has the same angular velocity as the crank, but whosephase is 90 behind the crank or eccentric. In this position thehorizontal movement of the weight Q is always in the opposite directionto that of the swinging aw. The amount oi this weight is so selectedthat, when 0 equals 180, its maximum inertia value horizontally shall beonehall the inertia of the jaw at zero degrees. l i eight Q wouldproduce horizontal lorces represented by curve F and the combinedeil'ect is represented by curve Flt which is the algebraic sum of curvesF and F. The resulting effect of applying the single unbalanced weightwill be a rythmic horizontal vibration having two maximum positivevalues and two maximum negative values for each revolution of thecrank-shaft (see curve FR). As a consequence, this rhythmic vibrationmay be reduced to Zero by the application of a second unbalancedrevolving weight having an angular velocity of twice that of theeccentric or crank, and so proportioned and related in phase (see curveF) as to oppose and balance the rhythmic force produced by the combinedaction of the oscillating jaw and the unbalanced weight Q. I, therefore,rovide a second unbalanced weight I which is arranged as nearly as convenient in the same vertical plane as the weight Q, and is mounted so asto rotate about an axis 23 at double the angular velocity of the shaft17, this being readily accomplished by a pair of two-to-one gears 24 andcarried by the crank-shaft 17 and the shaft 23 respectively.

The equations for the several curves are found as follows:

Let P be the stress in the pitman D-T.

" R at the end of thetoggle a angle of the toggle link with a linejoining the ends of the toggle link A and C.

Then P =2 R sin a.

The eccentricity of the crank OD is always small compared with thelength of the pitman so that Bx the moment of P about the center 0 andmust be equaled by the moment of the belt pull about the same center.Let the value of the belt pull reduced to the radius D O or 1 berepresented by B, then B?" =Pa;. But 95 1" sin 0, therefore B =Psin 0 or2 R sin au sin 6 I toggle joint B Z is equal to the travel of the crankF g and at any instant the distance yu or ZT='r+r cos 0. But

Introducing this value of sin a we have Bl SE17? design and are constantso that We may take 1 for the toggle length and 1 =lc. Then sin 0(1 +cos0) sin 0( 1+ cos 6) and the actual velocity of the jaw would be had bymultiplying this value by the actual velocity of the crank 12 or vsinfl(1 +cos 0) 7c The rate of change of this velocity or the ac celerationof the jaw f is given by the first differential of this velocity. o L..

Jaw velocity (cos 0 cos 0 sin 0):

The movement of the point D is supposed to be uniform and the spacemoved in (Z 25 would be (M and then f becomes The force required toproduce this acceleration in a weight VI will be 2 1x: 3%(cos 6+2 0 Butcos 6 may bel'in such phaseias to give I an effect opposedito theinertia of the jaw The values of r and B C are fixed by the and cantherefore be called cos 6. v:v=r :r or

Therefore The Weight WV is to be so selected that the force F shall beone half F when each is a maximum. F is a max. when 0 is zero andbecomes 9 2 F t WP.

gkr.

Therefore F as a max.

g gkr F is also a max. when 0 is zero. Therefore Flair: J gr glcr andW1" 2W r W 7' With this value of vV,

F cos 0 the resultant F R of the two forces F and F will be theiralgebraic sum and will he The secondary weight I has a horizontalaccelerating force F which in amount and direction shall be equal to Fwhen 0 is zero. The angular velocity is to be twice that of 0. Therefore0=20. Let the velocity be i) and radius r then (2 cos I) 1).

Let the weight be TV. Then VV/I DI/2 F= cos2 0.

Also

and at zero degrees when F is a max.

W"4o 1' W12 W F 57k? and W r 1/ W 47c1- With this value of \V F: cos 2 0g k r whichcan be written in the form F (cos sin Since -sin =cos 1 thiscan be changed to the form Combining this value with the resultant F toform a new final resultant the value is found to be zero for all valuesof 0.

The construction just described is designed for use with that type ofcrusher in which the jaw is given one complete oscillation foreachrotation of the crank-shaft, this being the general type. I find,however, that, where the throw of the eccentric is increased so as toswing the toggle an equal amount to each side of a line joining theouter ends of the toggle, the horizontal forces of the swinging jaw arethemselves rhythmic, giving two complete alternations for each rotationof the crank-shaft. Consequently in this type of machine, as illustrateddiagrammatically in Fig. 4, the unbalanced weight Q may be omitted andthe horizontal forces balanced by the single unbalanced weight I havingtwice the angular velocity of the crank-shaft.

Referring to Fig. 4 the following equations 'are found. 11011 the crankhas moved 0 degrees B will be at 3 distance from the medial line A G.Then 8 cos 0 8 and b sin a or r008 sin a i. R Loos sin 0 From thisrenirsinficosll Therefore P sin r=Br or and using the same significancefor 16 as bez'would be proportional to the reciprocal of fore theresistance sin 6 cos 6' As before. if B is the velocity of thejaw thisor The first difierential of this would give the acceleration of the jawwhich is as follows.

dV=cvcZ (sin 6 cos 6) =c'v(sin 6d cos 6+cos 6d sin 6) =cv(sin 6d 6+ cos6026) but (76 and sin 6 cos 6 1. Therefore this reduces to 2 Z (2 cos6 1) =3? (cos 2 6).

This value of the acceleration of the jaw is seen to agree with that ofF or J. and can therefore be balanced with the single weight revolvingwith the double angular velocity.

In order to protect the driving mechanism in case of sudden stoppage ofthe crusher it may sometimes be desirable to drive the weight I througha spring or similar yielding part 30.

I claim as my invention:

1. In a machine having a reciprocating jaw and rotating means fordriving the same, an unbalanced weight revolving at an angular velocitygreater than the angular velocity of the j aw-driving means, and in suchphase as to oppose the maximum acceleration thereof.

2. In a machine having a horizontally reciprocating jaw and rotary meansfor driving the same, a revolving unbalanced weight vertically revolvingat an angular velocity greater than the angular velocity of thejawdriving means and in such phase as to oppose the maximum accelerationthereof.

3. In a machine having a reciprocating jaw, a crank-shaft, andintermediate connections between said crank-shaft and said jaw foroperating same, an unbalanced weight revolving with an angular velocityequal to the angular velocity of the crank-shaft and in a phase behindthe phase of the crank, a second unbalanced weight, and means forrevolving said second unbalanced weight with double the angular velocityof the first unbalanced weight.

4. In a machine having a horizontally reciprocating jaw, a crank-shaft,and intermediate connections between said crankshaft and said jaw foroperating same, an unbalweight, and means for revolvlng said weight 5with an angular velocity equal to the angular anced weight revolvingvertically with an angular velocit T equal to the angular velocity ofthe crank-shaft and in a phase behind the phase of the crank, a secondunbalanced weight, and means for revolving said second unbalanced weightwith double the angular velocity of the first unbalanced weight.

5. In a machine having a reciprocating jaw and rotating means fordriving the same, a revolving unbalanced weight, and means for revolvingsaid weight at double the angular velocity of the jaw driving means.

6. In a machine having a horizontally reciprocating jaw and rotatingmeans for driving the same, a vertically revolving unbalanced weight,and means for revolving said weight at double the angular velocity ofthe jaw driving means.

7. In a crusher, a reciprocating jaw, a toggle for operating the same, adriving shaft, a crank and pitman connection between said driving shaftand toggle, a revolving unbalanced weight, and means for revolving saidweight at an angular velocity greater than the angular velocity of thedriving shaft and in such phase as to oppose the maximum accelerationthereof.

8. In a crusher, a reciprocating jaw, a toggle for operating the same, adriving shaft, a crank and pitman connection between said driving shaftand toggle, a vertical revolving unbalanced weight, and means forrevolving said weight at an angular velocity double the angular velocityof the main drive shaft.

9. In a crusher, a reciprocating jaw, a toggle for operating same, adrive shaft, a crank and pitman connection between said drive shaft andtoggle, an unbalanced vertically revolving weight revolving at anangular velocity equal to the angular velocity of the drive shaft and inthe phase behind the phase of the crank thereof, a second unbalancedweight, and means for revolving said second unbalanced weight in asubstantially vertical plane at double the angular velocity of the firstunbalanced weight.

10. In a crusher having a jaw, a crank shaft, intermediate connectionsbetween said crank shaft and said jaw for operating the same, anunbalanced vertically revolving velocity of the crank shaft and in aphase behind the phase of the crank.

11. In a crusher having a jaw, a crank shaft, intermediate connectionsbetween said my hand and seal at Houghton, Michigan, crank shaft andsaid jaw for 0 erating the this 25th day of January, A. D. one thousand1e same;i an unbalanced Vertical y revolvillllg nine hundred and six.Wei t, and means for revo vin said wei t 7 witl l an angular velocityequal t% the angu lar O/JNI HOOD velocity of the crank shaft and in aphase 90 Witnesses: degrees behind the phase of the crank. GEO. L.CHRISTENSEN,

In witness whereof, I, have hereunto set HARRY SHARP.

